JPH034797Y2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION This invention relates to an operation control device for controlling the operation of a fluid transport machine that is rotationally driven by an electric motor.

For example, large exhaust fans used in factories for environmental protection often require intermittent driving. For example, a large exhaust fan in a coke manufacturing plant needs to be driven to remove the large amount of dust produced only when the coke is transferred from the coke oven to a transport vehicle, and a large exhaust fan in a rolling mill needs to be driven to remove the large amount of dust produced only when the coke is transferred from the coke oven to the transport vehicle. In order to exhaust the large amount of water vapor produced only when cooling water is applied, large exhaust fans are required to be driven, and in addition, large exhaust fans installed in the load test section of assembled cars at automobile manufacturing plants are used to Since load tests are performed on multiple vehicles at once, driving is required only during the same load test. On the other hand, this kind of factory tends to generate dust from various causes and exhaust gas from the use of fuel, so exhaust is required almost constantly for environmental protection.

Due to the above-mentioned circumstances, factories that require large exhaust fans generally place large exhaust fans and small exhaust fans side by side, with the small exhaust fan running all the time and the large exhaust fan only being driven when necessary. That's what I do. However, as is well known, it is difficult to start a large electric motor for driving a large exhaust fan, and accidents such as breakage of the motor shaft during startup may occur. However, if a large exhaust fan is driven all the time and a small exhaust fan is also eliminated, power consumption will significantly increase and noise will become severe.

A possible solution would be to eliminate the small exhaust fan and drive the large exhaust fan at high speed only when necessary and at low speed at other times. In this case, rather than eliminating the need for a small exhaust fan, the fact that the drive load of the exhaust fan is proportional to the cube of the rotational speed significantly reduces power consumption, which significantly reduces production costs. It is lowered to the width.

By the way, the dust and exhaust gas that are conventionally emitted using small exhaust fans are not always emitted at a constant rate in a factory.
In order to reduce power consumption, the large exhaust fan that is driven as described above should be driven at low speed, depending on the rate of dust and exhaust gas generated in the factory. It would be desirable to change the drive rotation speed in the range.

The above-mentioned circumstances also apply to cooling water pumps and blowers that are driven by electric motors to transport cooling water in large air conditioning equipment, and at the beginning of cooling or heating operation, they rotate at high rotation speeds. Since the motor requires driving and can be driven at a low rotational speed once it enters a steady state, it is desirable to drive in a high speed range and drive in a low speed range in a manner that reduces power consumption.

In view of the above-mentioned circumstances, this invention aims to provide a new operation control device for a fluid transport machine that makes it possible to control the operation of the fluid transport machine in a manner that reduces power consumption the most. It is something to do.

Hereinafter, the invention will be explained in detail with reference to the illustrated embodiments.

In FIG. 1, reference numeral 1 denotes a large exhaust fan or its fan, which is an example of a fluid transport machine, and a large electric motor 2 is used to rotationally drive the fan shaft 1a.
is provided. According to this invention, a transmission 3 is inserted into the drive path of the fan shaft 1a by the electric motor 2. The transmission 3 has an input shaft 5 and an output shaft 6 that are rotatably supported by a transmission case 4, and the input shaft 5 is interlocked and connected to the motor shaft 2a of the electric motor 2 outside the transmission case 4 by a belt transmission mechanism. The output shaft 6 is interlocked and connected to the fan shaft 1a outside the transmission case 4 by a belt 8 transmission mechanism.

In the transmission case 4, between the input shaft 5 and the output shaft 6, there is a high-speed gear train formed by meshing a gear 9 loosely fitted to the input shaft 5 and a gear 10 fitted to the output shaft 6; Fitted gear 11 and output shaft 6
A low speed gear train is provided in which the gear 12 is meshed with the gear 12 loosely fitted in the gear 12. Accordingly, in the transmission 3, if the gear 9 is coupled to the input shaft 5, the output shaft 6, and therefore the fan shaft 1a, will be rotated at high speed, and the gear 12 will be coupled to the output shaft 5.
If the gears 9 and 12 are coupled to each other, the output shaft 6, and thus the fan shaft 1a, are rotated at gradually lower rotation speeds. In order to take part in transmission, a multi-disc hydraulic clutch 13 is mounted on the input shaft 5 and disposed on the gear 9, and a multi-disc hydraulic clutch 1 is disposed on the output shaft 6 and disposed on the gear 12.
4 are provided respectively.

Hydraulic oil is supplied to the two hydraulic clutches 13 and 14 in different ways, and FIG. 2 shows a hydraulic circuit for this purpose.

In FIG. 2, 15 is a hydraulic pump for supplying hydraulic oil from an oil tank 16 to the hydraulic clutches 13 and 14, and this hydraulic pump 15 is a first hydraulic pump.
As shown in the figure, it is installed on the outer surface of the transmission case 4 and is driven by the input shaft 5. Oil supply circuit 1 which is a discharge circuit of hydraulic pump 15
7 is set by a primary pressure regulating valve 19 in a drain circuit 18 branched from the circuit 17.

A four-port, two-position electromagnetic switching valve 20 is provided to selectively supply hydraulic oil to each hydraulic clutch 13, 14 to selectively operate each hydraulic clutch 13, 14. The two ports on the primary side of this electromagnetic switching valve 20 are connected to an oil drain circuit 21 that leads to the oil supply circuit 17 and the oil tank 16, and the two ports on the secondary side are connected to a hydraulic clutch, respectively. Supply/discharge circuits 22 and 23 which are led to 13 and 14 are connected. The electromagnetic switching valve 20 has a high-speed position H and a low-speed position L. At the high-speed position H, it connects the oil supply circuit 17 and the supply/discharge circuit 22, and also connects the supply/discharge circuit 23 and the oil discharge circuit 21, thereby controlling the hydraulic pressure. Only the clutch 13 is operated, and at the low speed position L, the oil supply circuit 17 and the supply/discharge circuit 23 are connected, and the supply/discharge circuit 22 and the oil discharge circuit 21 are connected, and only the hydraulic clutch 14 is operated. This electromagnetic switching valve 20 is normally in a low speed position L due to a bias from a spring 20a, and is moved to a high speed position H by excitation of a solenoid 20b.

Similarly, as shown in FIG. 2, the supply/discharge circuit 22 led to the hydraulic clutch 13 is directly connected to the hydraulic clutch 13, and at the high speed position H of the electromagnetic switching valve 20, the pressure is set by the primary pressure regulating valve 19. Hydraulic fluid is supplied to the hydraulic clutch 13 so that the hydraulic clutch 13 engages without slipping. That is, when the hydraulic clutch 13 on the high speed side of the transmission 3 is operated, the input shaft 5, which is the driving side rotating body,
The clutch is configured as a direct coupling type clutch that directly couples the gear 9 and the driven rotating body.

On the other hand, in the illustrated case, the supply and discharge circuit 23 leading to the hydraulic clutch 14 is provided with an oil supply circuit section 23A and an oil discharge circuit section 23B that are parallel to each other. , an electromagnetic flow rate adjustment valve 24 is inserted, and a drain circuit 26 into which a throttle 25 is inserted is connected. The oil supply circuit portion 23A is provided with a check valve 27 that allows oil to flow only in the direction of the hydraulic clutch 14, and the oil drain circuit portion 23B is provided with a check valve 28 that allows oil to flow only in the direction of the electromagnetic switching valve 20. , respectively, but since the electromagnetic flow rate adjustment valve 24 and the drain circuit 26 are installed as described above, the following procedure should be performed for the hydraulic clutch 14 when the electromagnetic switching valve 20 is in the low speed position L. Hydraulic oil will be supplied accordingly. That is, while the electromagnetic flow regulating valve 24 throttles the oil flow on its primary side and guides it to the secondary side, the oil flow from the oil supply circuit section 23A on the secondary side of the regulating valve 24 passes through the drain circuit 26 and at the throttle 25. Since oil is constantly drained at a determined rate, the electromagnetic flow rate adjustment valve 24
Hydraulic clutch 1 from secondary side oil supply circuit part 23A
The hydraulic pressure of the hydraulic oil supplied to the hydraulic clutch 1 becomes lower than the value set by the primary pressure regulating valve 19, and this low hydraulic pressure acts on the hydraulic clutch 1.
4 is operated in a slip state in which the friction elements are in slip engagement. The slip rate of the hydraulic clutch 14 can be freely changed since the adjusted flow rate set for the electromagnetic flow rate adjusting valve 24 is variable. In this way, the hydraulic clutch 14 on the low gear side of the transmission 3 slips the gear 12, which is a driving side rotating body, and the output shaft 6, which is a driven side rotating body, by its slip engagement with a variable slip rate. It is constructed with a slip-type hydraulic clutch with variable slip engagement.

As shown in FIG. 2, an electric controller 29 is provided, and the electric controller 29 receives a high-speed drive signal sg ₁ from a high-speed drive detection sensor 30 (for example, linked to a coke oven open switch). A pollution amount signal _sg2 from a pollution amount sensor 31 that detects the amount of dust (or carbon dioxide) in the factory is input. When the high-speed drive signal sg ₁ is input, the electric controller 29 outputs a solenoid excitation signal sg ₃ to excite the solenoid 20b of the electromagnetic switching valve 20, and when the high-speed drive signal sg 1 is not input, it outputs a solenoid excitation signal sg ₃ to excite the solenoid 20b of the electromagnetic switching valve 20. A flow rate adjustment signal sg ₄ having a value corresponding to the amount signal sg ₂ is output, and the set adjustment flow rate to the electromagnetic flow rate adjustment valve 24 is adjusted based on the slip rate (dust amount) relative to the amount of dust detected by the pollution amount detection sensor 31. The hydraulic clutch 14 is configured to perform change control so that the hydraulic clutch 14 is brought into slip engagement (the greater the slip rate, the smaller the slip ratio).

In addition, in FIG. 2, 32 is the primary pressure regulating valve 19.
A secondary pressure regulating valve inserted into the drain circuit 18 on the secondary side of the lubricating oil is guided to parts that require lubrication, such as the friction elements of the hydraulic clutches 13 and 14 and the bearings of the output shafts 5 and 6. This is for setting the oil pressure of the supply circuit 33. Further, 34 is the primary side of the electromagnetic flow rate adjustment valve 24 and the oil supply circuit portion 23A.
This is a fine-mesh line filter inserted into the line filter 34 to protect the electromagnetic flow rate adjustment valve 24.
It is provided so that oil can be quickly drained from the hydraulic clutch 14 without passing through the hydraulic clutch 14.

The illustrated large-scale exhaust fan operation control device according to this invention is constructed as described above, so that when the large-scale exhaust fan needs to be driven at high speed, a solenoid excitation signal from the electric controller 29 is sent.
The output of sg ₃ moves the electromagnetic switching valve 20 to the high-speed position H, and the hydraulic clutch 13 is operated to cause the high-speed gear trains 9 and 10 of the transmission 3 to perform speed change transmission, and the fan shaft 1a is driven at high speed. hand,
A high rate of exhaust air is carried out. In addition, normally, the electromagnetic switching valve 20 is in the low speed position L, the hydraulic clutch 14 is operated, and the low speed gear trains 11 and 12 of the transmission 3 perform gear transmission.
Since the adjusted flow rate of the electromagnetic flow rate adjustment valve 24 is controlled by sg ₄ , the slip rate of the hydraulic clutch 14 is set to a value commensurate with the amount of contamination, and the driving rotation speed of the fan shaft 1a is set in a low speed range to correspond to the amount of contamination. The rotation speed is controlled to change to the specified rotation speed.

In the above embodiment, the clutch for the high speed gear train is replaced with the hydraulic clutch 1 for the low speed gear train.
The hydraulic clutch 13 was constructed because the main parts of the operating mechanism and the operating mechanism for the gear train 4 can be shared, but the clutch for this high-speed gear train is
Any clutch, such as a mechanical or electromagnetic type, may be used as long as it can directly connect the driving side rotary body and the driven side rotary body. Further, the flow rate regulating valve 24 is used to slip engage the hydraulic clutch 14 for the low-speed gear train, but the primary pressure regulating valve 19 may be a proportional solenoid valve, or the oil supply circuit 17 or the supply/discharge circuit 23 may be equipped with an electromagnetic pressure reducing valve. A valve may be inserted to provide a variable low oil pressure to cause the hydraulic clutch 14 to slip into engagement with a variable slip rate.

It goes without saying that this invention can be implemented not only for large-sized exhaust fans, but also for other fluid transport machines such as pumps and blowers.

As is clear from the above description, the operation control device for a fluid transport machine of this invention selectively changes speed by operating a clutch during the drive path of the fluid transport machine 1 which is rotationally driven by an electric motor 2. A transmission 3 having a high speed gear train 9, 10 and a low speed gear train 11, 12 for transmitting power is inserted and installed, and a clutch for the high speed gear train is directly connected to its driving side rotating body 5 and driven side rotating body 9. A slip-type hydraulic clutch 14 is constructed in which a clutch for a low-speed gear train is slip-engaged between a driving-side rotating body 12 and a driven-side rotating body 6 at a variable slip rate.
It has the following advantages:

That is, in the operation control device of this invention, when the clutch 13 for the high speed gear train is actuated, the fluid transport machine is driven at high speed, and when the hydraulic clutch 14 for the low speed gear train is activated, the fluid transport machine is driven at low speed. This eliminates the need for a small fluid transport machine and its drive mechanism, and allows the fluid transport machine to transport a large amount of fluid only when necessary by repeatedly starting and stopping a large electric motor that is difficult to start. However, the power consumption can be greatly reduced for the following reasons.

In other words, since the fluid transport machine is driven at high speed only when necessary as described above, power consumption is already greatly reduced.
Since the slip rate can be changed and controlled by changing the slip rate, it is possible to control the drive rotation speed in the same low speed range to the minimum value that is appropriate for the amount of dust, amount of exhaust gas, or temperature conditions, and thereby reduce power consumption. In addition, it has been reported that there is a maximum energy loss of about 15% when a hydraulic clutch is slip-engaged, so only one hydraulic clutch for slip-engagement can be inserted and installed in the drive path. When attempting to obtain high-speed drive and low-speed drive of a fluid transport machine exclusively by changing the slip rate of the single hydraulic clutch, the energy loss due to clutch slip engagement becomes large; Since the low two-speed transmission 3 is provided and the rotational speed control in the low speed range is obtained only by the slip engagement of the hydraulic clutch 14, energy loss due to the slip engagement of the hydraulic clutch 14 can be kept small. This can further reduce power consumption.

However, as mentioned above, it is possible to reduce power consumption by using the slip type hydraulic clutch 14 exclusively for the low speed range, without providing a hydraulic clutch that slips in the entire speed range. According to this invention, the slip type hydraulic clutch 14 described above can be made compact, and the cooling device for suppressing heat generation due to slip engagement can also be made small. Become.

[Brief explanation of the drawing]

FIG. 1 is a schematic vertical sectional view showing an embodiment of this invention, and FIG. 2 is a circuit diagram of a hydraulic circuit and a block diagram of an electric control mechanism in the same embodiment. 1... Large exhaust fan (fan), 1a... Fan shaft, 2... Electric motor, 3... Transmission, 5... Input shaft, 6... Output shaft, 7, 8... Belt, 9, 1
0, 11, 12... Gear, 13, 14... Hydraulic clutch, 17... Oil supply circuit, 19... Primary pressure regulating valve, 20... Solenoid switching valve, 21... Oil drain circuit, 2
2, 23... Supply and exhaust circuit, 24... Solenoid flow rate adjustment valve, 25... Throttle, 26... Drain circuit, 29...
...Electric controller, 30... High-speed drive detection sensor, 31... Pollution amount detection sensor.

Claims (1)

[Scope of utility model registration request] A transmission equipped with a high-speed gear train and a low-speed gear train, each of which selectively transmits gear changes through the operation of a clutch, is inserted into the drive path of a fluid transport machine that is rotationally driven by an electric motor. The clutch for the low-speed gear train is configured as a direct-coupling clutch that directly connects the driving side rotating body and the driven side rotating body, and the clutch for the low speed gear train is configured to have a variable slip ratio between the driving side rotating body and the driven side rotating body. An operating control device for a fluid transport machine comprising a slip-type hydraulic clutch that is slip-engaged.